US20040185984A1 - Multi-speed power transmission - Google Patents
Multi-speed power transmission Download PDFInfo
- Publication number
- US20040185984A1 US20040185984A1 US10/391,834 US39183403A US2004185984A1 US 20040185984 A1 US20040185984 A1 US 20040185984A1 US 39183403 A US39183403 A US 39183403A US 2004185984 A1 US2004185984 A1 US 2004185984A1
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- US
- United States
- Prior art keywords
- mechanical clutch
- ring gear
- clutch means
- sun gear
- planetary gearset
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/62—Gearings having three or more central gears
- F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
- F16H3/663—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another with conveying rotary motion between axially spaced orbital gears, e.g. RAVIGNEAUX
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/0069—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising ten forward speeds
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
- F16H2200/2007—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with two sets of orbital gears
Definitions
- This invention relates to power transmissions and, more particularly, to power transmissions employing a plurality of mechanical clutches and planetary gearing.
- Multi-speed power transmissions which employ mechanical clutches such as synchronizers, generally include pairs of meshing gears to establish drive or speed ratios between a transmission input shaft and a transmission output shaft. These transmissions require a pair of meshing gears for each of the forward drive ratios and one and a half pairs of gears for the reverse ratio.
- Each of the gear pairs includes a synchronizer or mechanical clutch, which engages one of the gears with either the main shaft or the countershaft while the other gear of that mesh is continuously driven by or with one of the other shafts.
- a ten speed transmission having a single reverse would require ten and a half pairs of gears, at least ten synchronizers, and a movable idler gear for the reverse ratio.
- the reverse ratio normally would include the input gear for first gear and an idler gear and a separate output gear.
- the reverse ratio is relatively close to or nearly equal to the numerical value of the first ratio.
- the present invention seeks to provide a multi-speed transmission having two planetary gearsets and a plurality of mechanical clutch mechanisms.
- the transmission includes two planetary gearsets each of which is a simple planetary gearset.
- the transmission has incorporated therein two three-way synchronizers and three two-way synchronizers, which are effectively controlled to provide ten forward speed ratios and one reverse speed ratio between an input shaft and an output shaft.
- one of the planetary gearsets includes a sun gear member and two identical ring gear members.
- one of the planetary gearsets includes two identical sun gear members and one ring gear member.
- the dual ring gear members and dual sun gear members of each of the planetary gearsets is provided to permit input and output drives from more than one of the planetary members.
- FIG. 1 is a schematic representation of a powertrain having a transmission incorporating the present invention.
- FIG. 2 is a chart describing the engagement sequence of the mechanical clutches employed with the transmission shown in FIG. 1.
- FIG. 1 a powertrain 10 having an engine 12 , a power transmission 14 , and a conventional final drive mechanism 16 .
- the engine 12 is a conventional internal combustion engine.
- the transmission 14 has an input clutch 18 , a pair of planetary gearsets 20 and 22 , and five mechanical clutches or synchronizers 24 , 26 , 28 , 30 , and 32 .
- the mechanical clutch 24 has an input portion 24 A and three output positions 24 B, 24 C, and 24 D.
- the input portion 24 A is continuously connected through an input shaft 34 with the input clutch 18 , which is a conventional friction type clutch, which might be either fluid engaged or mechanically engaged. Such clutches and their operation are well known in the art of power transmissions.
- the input portion 24 A is selectively connectible with each of the output portions 24 B, 24 C, and 24 D.
- the mechanical clutch 24 is a rotating type torque transmitting mechanism.
- the mechanical clutch 26 has an output portion 26 A and two input positions 26 B and 26 C.
- the mechanical clutch 26 is a rotating type torque transmitting mechanism.
- the mechanical clutch 28 has a ground portion 28 A and three input positions 28 B, 28 C, and 28 D.
- the mechanical clutch 28 is a stationary type torque transmitting mechanism.
- the mechanical clutch 30 has an input portion 30 A and two output portions 30 B and 30 C.
- the mechanical clutch 30 is a dual position synchronizer in which the input portion 30 A may be connected to each of the output portions 30 B and 30 C individually and connected to both of the portions 30 B and 30 C simultaneously.
- the mechanical clutch 30 is a rotating type torque transmitting mechanism.
- the mechanical clutch 32 has a ground portion 32 A and two input positions 32 B and 32 C.
- the mechanical clutch 32 is therefore a stationary torque transmitting mechanism.
- the planetary gearset 20 has a sun gear member 36 , ring gear members 38 , and a planet carrier assembly member 40 .
- the planet carrier assembly member 40 includes a plurality of pinion gears 42 , which are rotatably disposed on a planet carrier member 44 and placed in meshing relationship between the sun gear member 36 and the ring gear members 38 .
- the planet carrier member 44 is continuously connected with the position 24 C of mechanical clutch 24 and the position 28 C of the mechanical clutch 28 .
- the sun gear member 36 is continuously connected with the position 24 B and with the position 28 B.
- One of the ring gear members 38 is continuously connected with the position 28 B and the other ring gear member 38 is continuously connected with the position 24 C.
- the ring gear members 38 are identical in construction, each therefore having the same number of teeth and meshing with an elongated pinion 42 .
- the input portion 24 A of mechanical clutch 24 is continuously connected with the input shaft 34 , as previously mentioned, the ground position 28 A of the mechanical clutch 28 is connected with a stationary portion or housing 46 of the transmission 10 .
- One ring gear member 38 is continuously connected with both the position 24 D of synchronizer 24 , and position 26 C of synchronizer 26 .
- the synchronizers 26 and 30 are continuously interconnected by their respective portions 26 A and 30 A.
- the planetary gearset 22 has split sun gear members 48 , a ring gear member 50 , and a planet carrier assembly member 52 .
- the planet carrier assembly member 52 has a plurality of pinion gears 54 rotatably mounted on a planet carrier member 56 and disposed in meshing relationship between the split sun gear members 48 and the ring gear member 50 .
- the planet carrier member 56 is continuously drivingly connected with a transmission output shaft 58 , which in turn is connected with the final drive mechanism 16 .
- the ring gear member 50 is continuously connected with the position 30 B of synchronizer 30 and with the position 32 B of the synchronizer 32 .
- One sun gear member 48 is connected continuously with the position 30 C of synchronizer 30 and the other portion of sun gear member 48 is connected with the position 32 C of the synchronizer 32 .
- the ground portion 32 A of the synchronizer 32 is continuously connected with the stationary portion 46 .
- the synchronizers or mechanical clutches are selectively controlled to establish ten forward speed ratios and a reverse speed ratio between the input shaft 34 and the output shaft 58 .
- S 1 is the sun gear member 36
- R 1 is the ring gear member 38
- C 1 is the planet carrier member 44
- S 2 is the sun gear members 48 and R 2 is the ring gear member 50 .
- the synchronizers 28 and 32 are shown as open in several of the transmission ratios. This indicates that the synchronizer 28 , for example, does not ground any member and the synchronizer 32 does not ground any member.
- the synchronizer 28 is open, the planetary gearset 20 is in a neutral or 1:1 condition, and when the synchronizer 32 is open, the planetary gearset 22 is also in a neutral or 1:1 condition.
- the synchronizer 24 is effective to connect each of the members 36 , 38 , and 44 individually with the input shaft 34 , which is then connected with the engine 12 through the judicious engagement of the clutch 18 .
- the synchronizer 30 is effective in fourth, sixth, eighth, and tenth ratios to interconnect the ring gear member 50 with the sun gear members 48 thereby placing the planetary gearset 22 in a 1:1 condition. Note that to place the planetary gearset 20 in a 1:1 condition, the planet carrier member 44 is connected to both the synchronizer 24 and the synchronizer 26 . This connects the input shaft 34 directly with the synchronizer 26 to the planet carrier member 44 .
- the chart of FIG. 2 also describes an example of the numerical values for the ratios that are available with the transmission described in FIG. 1.
- the multi-speed transmission 10 employs two simple planetary gearsets and five synchronizers to accomplish ten forward speed ratios and a reverse speed ratio.
- the planetary gearsets 20 and 22 are both simple planetary gearsets, that is, there is a single gear mesh at the sun gear and at the ring gear member by a single pinion member.
- the planet carrier member will have mounted thereon a plurality of pinion gears to equally distribute the torque loads between the sun gear member and the ring gear member. In any event, there is only one active mesh between the pinion and the sun gear member and between the pinion and the ring gear member.
- the use of a second identical sun gear member and ring gear member is incorporated to allow the proper connections of input, output, and ground as required for the various ratios of the transmission.
- Simple planetary gearsets significantly reduces the manufacturing complexities as well as assembly complexities and the overall cost of a power transmission. Simple planetary gearsets also have an advantage of reduced pinion to carrier speeds and reduced torque related losses.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
Description
- This invention relates to power transmissions and, more particularly, to power transmissions employing a plurality of mechanical clutches and planetary gearing.
- Multi-speed power transmissions, which employ mechanical clutches such as synchronizers, generally include pairs of meshing gears to establish drive or speed ratios between a transmission input shaft and a transmission output shaft. These transmissions require a pair of meshing gears for each of the forward drive ratios and one and a half pairs of gears for the reverse ratio. Each of the gear pairs includes a synchronizer or mechanical clutch, which engages one of the gears with either the main shaft or the countershaft while the other gear of that mesh is continuously driven by or with one of the other shafts.
- For example, a ten speed transmission having a single reverse would require ten and a half pairs of gears, at least ten synchronizers, and a movable idler gear for the reverse ratio. The reverse ratio normally would include the input gear for first gear and an idler gear and a separate output gear. Thus, the reverse ratio is relatively close to or nearly equal to the numerical value of the first ratio.
- More recently, it has been proposed to include planetary gearing in manual type transmissions. In these transmissions, multiple planetary gearsets are included. In each of the transmissions, at least one of the gearsets is a compound gearset. As is well known, compound gearsets require additional pinion sets, which increase the complexity and overall cost of a planetary gearset.
- The present invention seeks to provide a multi-speed transmission having two planetary gearsets and a plurality of mechanical clutch mechanisms.
- It is therefore an object of the present invention to provide an improved multi-speed power transmission.
- In one aspect of the present invention, the transmission includes two planetary gearsets each of which is a simple planetary gearset.
- In another aspect of the present invention, the transmission has incorporated therein two three-way synchronizers and three two-way synchronizers, which are effectively controlled to provide ten forward speed ratios and one reverse speed ratio between an input shaft and an output shaft.
- In a further aspect of the present invention, one of the planetary gearsets includes a sun gear member and two identical ring gear members.
- In yet a further aspect of the present invention, one of the planetary gearsets includes two identical sun gear members and one ring gear member.
- In a yet still further aspect of the present invention, the dual ring gear members and dual sun gear members of each of the planetary gearsets is provided to permit input and output drives from more than one of the planetary members.
- FIG. 1 is a schematic representation of a powertrain having a transmission incorporating the present invention.
- FIG. 2 is a chart describing the engagement sequence of the mechanical clutches employed with the transmission shown in FIG. 1.
- Referring to the drawings, there is seen in FIG. 1 a
powertrain 10 having anengine 12, apower transmission 14, and a conventionalfinal drive mechanism 16. Theengine 12 is a conventional internal combustion engine. Thetransmission 14 has aninput clutch 18, a pair ofplanetary gearsets synchronizers - The
mechanical clutch 24 has aninput portion 24A and threeoutput positions input portion 24A is continuously connected through aninput shaft 34 with theinput clutch 18, which is a conventional friction type clutch, which might be either fluid engaged or mechanically engaged. Such clutches and their operation are well known in the art of power transmissions. Theinput portion 24A is selectively connectible with each of theoutput portions mechanical clutch 24 is a rotating type torque transmitting mechanism. - The
mechanical clutch 26 has anoutput portion 26A and twoinput positions mechanical clutch 26 is a rotating type torque transmitting mechanism. - The
mechanical clutch 28 has aground portion 28A and threeinput positions mechanical clutch 28 is a stationary type torque transmitting mechanism. - The
mechanical clutch 30 has aninput portion 30A and twooutput portions mechanical clutch 30 is a dual position synchronizer in which theinput portion 30A may be connected to each of theoutput portions portions mechanical clutch 30 is a rotating type torque transmitting mechanism. - The
mechanical clutch 32 has aground portion 32A and twoinput positions mechanical clutch 32 is therefore a stationary torque transmitting mechanism. - The
planetary gearset 20 has asun gear member 36,ring gear members 38, and a planetcarrier assembly member 40. The planetcarrier assembly member 40 includes a plurality ofpinion gears 42, which are rotatably disposed on aplanet carrier member 44 and placed in meshing relationship between thesun gear member 36 and thering gear members 38. - The
planet carrier member 44 is continuously connected with theposition 24C ofmechanical clutch 24 and theposition 28C of themechanical clutch 28. Thesun gear member 36 is continuously connected with theposition 24B and with theposition 28B. One of thering gear members 38 is continuously connected with theposition 28B and the otherring gear member 38 is continuously connected with theposition 24C. Thering gear members 38 are identical in construction, each therefore having the same number of teeth and meshing with anelongated pinion 42. Theinput portion 24A ofmechanical clutch 24 is continuously connected with theinput shaft 34, as previously mentioned, theground position 28A of themechanical clutch 28 is connected with a stationary portion orhousing 46 of thetransmission 10. - One
ring gear member 38 is continuously connected with both the position 24D ofsynchronizer 24, andposition 26C ofsynchronizer 26. Thesynchronizers respective portions - The
planetary gearset 22 has splitsun gear members 48, aring gear member 50, and a planetcarrier assembly member 52. The planetcarrier assembly member 52 has a plurality ofpinion gears 54 rotatably mounted on aplanet carrier member 56 and disposed in meshing relationship between the splitsun gear members 48 and thering gear member 50. Theplanet carrier member 56 is continuously drivingly connected with atransmission output shaft 58, which in turn is connected with thefinal drive mechanism 16. - The
ring gear member 50 is continuously connected with theposition 30B ofsynchronizer 30 and with theposition 32B of thesynchronizer 32. Onesun gear member 48 is connected continuously with theposition 30C ofsynchronizer 30 and the other portion ofsun gear member 48 is connected with theposition 32C of thesynchronizer 32. Theground portion 32A of thesynchronizer 32 is continuously connected with thestationary portion 46. - As seen in the chart of FIG. 2, the synchronizers or mechanical clutches are selectively controlled to establish ten forward speed ratios and a reverse speed ratio between the
input shaft 34 and theoutput shaft 58. In the chart of FIG. 2, the terminology S1 is thesun gear member 36, R1 is thering gear member 38, and C1 is theplanet carrier member 44. Also in the chart, S2 is thesun gear members 48 and R2 is thering gear member 50. Thesynchronizers synchronizer 28, for example, does not ground any member and thesynchronizer 32 does not ground any member. When thesynchronizer 28 is open, theplanetary gearset 20 is in a neutral or 1:1 condition, and when thesynchronizer 32 is open, theplanetary gearset 22 is also in a neutral or 1:1 condition. - The
synchronizer 24 is effective to connect each of themembers input shaft 34, which is then connected with theengine 12 through the judicious engagement of theclutch 18. Thesynchronizer 30 is effective in fourth, sixth, eighth, and tenth ratios to interconnect thering gear member 50 with thesun gear members 48 thereby placing theplanetary gearset 22 in a 1:1 condition. Note that to place theplanetary gearset 20 in a 1:1 condition, theplanet carrier member 44 is connected to both thesynchronizer 24 and thesynchronizer 26. This connects theinput shaft 34 directly with thesynchronizer 26 to theplanet carrier member 44. - The chart of FIG. 2 also describes an example of the numerical values for the ratios that are available with the transmission described in FIG. 1. Those skilled in the art will recognize that the
multi-speed transmission 10 employs two simple planetary gearsets and five synchronizers to accomplish ten forward speed ratios and a reverse speed ratio. - The
planetary gearsets - The use of simple planetary gearsets significantly reduces the manufacturing complexities as well as assembly complexities and the overall cost of a power transmission. Simple planetary gearsets also have an advantage of reduced pinion to carrier speeds and reduced torque related losses.
Claims (5)
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US10/391,834 US6786845B1 (en) | 2003-03-18 | 2003-03-18 | Multi-speed power transmission |
DE102004007004A DE102004007004A1 (en) | 2003-03-18 | 2004-02-12 | More speed power shift |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US10/391,834 US6786845B1 (en) | 2003-03-18 | 2003-03-18 | Multi-speed power transmission |
Publications (2)
Publication Number | Publication Date |
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US6786845B1 US6786845B1 (en) | 2004-09-07 |
US20040185984A1 true US20040185984A1 (en) | 2004-09-23 |
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Application Number | Title | Priority Date | Filing Date |
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US10/391,834 Expired - Fee Related US6786845B1 (en) | 2003-03-18 | 2003-03-18 | Multi-speed power transmission |
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US (1) | US6786845B1 (en) |
DE (1) | DE102004007004A1 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20050043134A1 (en) * | 2003-08-18 | 2005-02-24 | Toyota Jidosha Kabushiki Kaisha | Automatic transmission |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US7004881B2 (en) * | 2004-03-24 | 2006-02-28 | General Motors Corporation | Dual input clutch transmission having synchronizers for establishing speed ratios |
US7235032B2 (en) * | 2005-08-15 | 2007-06-26 | Ford Global Technologies, Llc | Multiple-speed automatic transmission having a two-speed input and a Simpson gearset |
RU2010107092A (en) * | 2010-02-25 | 2011-08-27 | Джи Эм Глоубал Текнолоджи Оперейшнз, Инк. (Us) | MULTI-SPEED PLANETARY GEARS WITH TWO BLOCKS OF TWO-SPEED PLANETARY GEARS |
US8444526B1 (en) * | 2012-04-05 | 2013-05-21 | The Gates Corporation | Multi-ratio planetary gear transmission |
Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20040023748A1 (en) * | 2002-08-02 | 2004-02-05 | Haka Raymond James | Multi-speed transmission |
-
2003
- 2003-03-18 US US10/391,834 patent/US6786845B1/en not_active Expired - Fee Related
-
2004
- 2004-02-12 DE DE102004007004A patent/DE102004007004A1/en not_active Withdrawn
Patent Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20040023748A1 (en) * | 2002-08-02 | 2004-02-05 | Haka Raymond James | Multi-speed transmission |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20050043134A1 (en) * | 2003-08-18 | 2005-02-24 | Toyota Jidosha Kabushiki Kaisha | Automatic transmission |
US7276011B2 (en) * | 2003-08-18 | 2007-10-02 | Toyota Jidosha Kabushiki Kaisha | Automatic transmission |
US20070287572A1 (en) * | 2003-08-18 | 2007-12-13 | Toyota Jidosha Kabushiki Kaisha | Automatic transmission |
US7488269B2 (en) | 2003-08-18 | 2009-02-10 | Toyota Jidosha Kabushiki Kaisha | Automatic transmission |
Also Published As
Publication number | Publication date |
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US6786845B1 (en) | 2004-09-07 |
DE102004007004A1 (en) | 2004-10-14 |
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